Compressor valve



P 15, 1964 c. H. cm 3,148,697

COMPRESSOR VALVE Filed Oct. 17, 1960 2 Sheets-Sheet 1 INVENTOR. E65. 4. v BYi/Z/Z d/i 647' ATTORNEY.

P 15, 1954 I c. H. CARR 3,148,697

COMPRESSOR VALVE Filed Oct. 17, 1960 2 SheetS-Snee'tY Q waw. a. aw

ATTORNEK frictional interference and turbulence.

United States Patent ()ftice amass?) Patented Sept. I5, 1954 3,148,697 GCGRZPRESSQR VALVE (Ilifiord H. Carr, 614 W. 67th St, Kansas City, Mo. Fiied 49st. 17, Unit, Ser. No. 63,113 Lil (1. 137-327) This invention relates generally to valves for gas compressors and refers more particularly to the provision of losses resulting from violent changes in flow direction,

Heretofore many of the factors which are involved in obtaining proper gas flow, as well as quick and positive action of the valves with low pressure dil ferentials, have been unrecognized or ignored. I have discovered that these factors are, however, of critical importance in attempting to obtain optimum capacity in high speed compressors. By high speed compressors I am referring to those compressors operating in the range of 400 to 1750 strokes per minute. By their nature, these compressors have a short stroke. Therefore they require for optimum performance valves which not only will permit flow of gas to and from the cylinder with a minimum of pressure loss and at high velocity, but which will also seat rapidly and positively at the critical pressure reversals which take place at the inception and completion of the suction and discharge strokes. Furthermore, such valves must be designed to provide a minimum clearance volume in the cylinder thus to promote as complete evacuation of the cylinder as possible during the discharge stroke.

One of the principle objects of the present invention is to provide a novel valve construction for high speed compressors which results in appreciably improved performance of the compressor. It is a particular-feature of the invention in this respect that the valve structure is such that the gas flow therethrough is carefully controlled and guided to obtain smooth, relatively nonturbulent movement combined with a relatively high velocity and with a low degree of kinetic energy loss.

A further object of the invention itto provide a valve structure of the character described which, by virtue of the flow control provided, assures a rapid and positive seating of the valve elements at low pressure differentials and in which the flow is so guided that there is little, if any resistance to seating as the flow tends to reverse therethrough.

Still another object of the invention is to provide a valve construction for high speed gas compressors in which the clearance volume is held to a low value, thus insuring of optimum evacuation of the cylinder during the discharge stroke.

A further object of the invention is to provide a valve structure of the character described, which is so constructed that it promotes the passage therethrough of particulate material such as flakes of carbon or other foreign matter which may, because of small size, pass the usual screen on compressors and become entrained in the gas on its way into or out of the cylinder.

the construction provided, is capable of being assembled with very few basic component parts and which lends itself readily to being formed by casting operations, thus eliminating the need for extensive machining.

A further object of the invention is'to provide a discharge valve structure for high speed compressors in which the valving elements are resiliently biased toward the seated position by a novel arrangement of springs and retaining supports therefor which permit the valve to be given a thickness which is considerably less than in presently known valves. It is a feature of the invention in this respect that the springs are self-cleaning and provide no opportunity for undesirable collection of dirt or foreign matter'which might otherwise render them inoperative.

A further object of the invention is to provide a suction valve structure which is ready for use as a replacement in presently operating compressors and which, by virtue of its construction has an approciably greater ratio of area open to gas flow to cross-sectional area of the valve than in presently known valves of this type. It is a feature of the invention in this respect that I have been able to provide a gasicompressor valve which requires Still another object of the invention is to provide a valve structure of the character described which, through no bolts to hold its constituent parts in assembled relation and in which the components are maintained in alignment in novel fashion both during installation and operation.

Further objects of the invention are to providecornpressor valve structures which can be readily installed in existing compressors; which are light in weight and have a minimum of moving parts; which are relatively easy to manufacture; and which are capable of withstanding rugged use for a long period.

Other and further objects of the invention together with the features of novelty appurtenant thereto will appear in the course of the following description.

in the accompanying drawings which form a part of the instant specification and are'to be read in conjunction therewith, and in which like reference numerals indicate like parts in the various views;

, FIG. 1 is a fragmentary side, elevation of the upper head portion of a typical compressor equipped with a discharge valve in accordance with the invention, parts being broken away and shown in section for purposes of illustration; q

FIG. 2 is a top plan view of the discharge valve, here shown disass'ociated from the compressor, portions of the top plate being broken away for purposes of illustration;

FIG, 3 is a bottom plan view of the discharge valve, parts of the base member being broken away for purposes of illustration.

, FIG. 3a is an enlarged fragmentary section taken along the line 3a3a of PEG. 3 in the direction of the arrows;

FIG. 4 is an enlarged fragmentary section taken along the line 44 of FIG. 2 in thedirection of the arrows;

FIG. 5 is an enlarged fragmentary section taken along the line 55 of FIG. 2 in the direction of the arrows;

FIG. 6 is an enlarged fragmentary section taken along the line 66 of FIG. 2 the direction of the arrows;

FIG. '7 is a top plan view of a suction valve embodying features of the invention, a portion of the top plate being broken away for purposes of illustration;

FIG. 8 is a bottom plan view of the suction valve of FIG. 7, portions of the bottom member being broken away with parts also shown in section for purposes of illustration; and V FIG. 9 isan enlarged section taken generally along the line 99 of FIG. 7 in the direction of the arrows.

Referring now to the drawings and initially to the embodiment of the invention disclosed in FIGS. 1 through 6; inclusive, illustrated in FIG. 1 is the upper head portion of the typical compressor having the inside cylinder wall 19. While not shown, it will be understood that a piston operates within the cylinder, moving upwardly on the compression stroke and downwardly on the suction stroke. The cylinder body is indicated by reference numeral 11 and it is provided with the discharge port 12 which communicates with the interior of the head. Forming the upper end of the cylinder is the head plate Iii-which seats at its margin on an annular shoulder 14.

Located in and carried by the head plate 13 are one or more discharge valves 15. While further description oi the valves will be given in connection with FIGS. 2 through 6, it is noted at this point that the valve is circular in configuration and seats in the corresponding aperture 17 formed in the head plate 13. To hold the valve assembly seated, there is provided a hold down ring 18 which engages the rim of the upper portion of the valve assembly and is interposed between the valve assembly and a hold down member 19. The hold down member 19 comprises an annular ring having the arched radial webs or spokes 26 which join centrally with a plug portion 21. A pressure plate 22 overlies the plug 21 and serves to transmit thereto the compressive force of a spring 23. The details of construction of the compressor play no part in the present invention and FIG. 1 is simply provided to illustrate the mounting of the valve structure of FIGS. 2 through 6 in a typical compressor.

Referring now to FIGS. 2 and 3, the basic components of the valve assembly comprise a pair of circular plates 24 and 25. The top plate is indicated by reference numeral 24 while thebottom plate or base member by reference numeral 25 The plates 24 and 25 have the smooth, fiat contacting faces 24a and 25a, respectively. The lower end of the bottom plate 25 is provided with a reduced diameter portion 25b which forms an annular shoulder 25c, adapted to seat upon a corresponding shoulder 130! formed in the head plate 13 of the compressor. While not secured against end-wise separation, the plates are prevented from twisting movement relative one another by a plurality of dowel pins 25d secured in and extending upwardly from the upper face of the lower plate member 25 and which are received in corresponding recesses 24b formed in the top plate member 24. It will be understood that the base and top are preferably formed from high quality steel or alloys which have good strength and hardness properties.

Formed within the basic valve members thus described and extending therethrough are a plurality of gas flow vents, each of which include an inlet passageway 26 which communicates internally of the valve assembly with an enlarged chamber containing a spherical ball-like valve element 27. In FIGS. 2 and 3 I have shown some of the chambers without the balls 27 therein, this being primarily for the purpose of understanding the construction of the chambers as later to be described. However, it will be understood that in a completed unit, each individual chamber contains a ball 2'7 and that there are as many balls as there are inlets 26.

As is believed evident, the upper ends of the inlet passageways 26 are normally closed by the ball elements 2'7. The inlet passageways 26 are so formed at their upper ends as to provide openings in the face 25a of the lower plate member in the form of recessed ball seats. The seat for the ball is indicated at 28. Leading upwardly and away from the seat is the smoothly curved expanding diameter surface 29 which intersects and forms a circular opening in face 24a of greater diameter than the ball. Thus the recess forms around the ball an annular space 30 which increases in cross-sectional area upwardly away from seat 28. The diameter of the upper end of surface 29 is such that the space between said end and the nearest portion of the ball, when the ball is lifted to the broken line position of FIGS. 5 and 6, is substantially equal to the space between the seat 28 and the nearest portion of the ball. The radius of curvature of surface 19 should be approximately at the midpoint of the ball when it is in its lifted position, as illustrated in FIG. 2, although it may be slightly thereabove in order to cause the space between the ball surface and recess surface 29 to increase slightly upwardly from the seat 28.

Formed in the lower face of the top plate 24 are a plurality of openings 31 which may be considered for purposes of description as the lower ends of cylindrical passageways 32, extending axially upwardly through the top plate. There is one such passageway for each ball 27. The diameter of the opening 31 is equal to that of the upper end of surface 29.

Formed integral with and extending radially inwardly from the wall of each passageway 32 are a plurality of vertically oriented, peripherally spaced ball guides 33. As best seen in FIG. 3a, each guide is tapered in thickmess, the smaller end being adjacent the opening 31. The inner surfaces 33a of the guides, that is, those surfaces confronting the ball, run parallel with the axis of the passageway for a substantial portion of their length and then converge inwardly in curved transition portions 33a to merge with a central, upper, ball stop 34 positioned axially in the path of the ball.

The depth of guides 33 relative to the wall of passageway 32 is preferably such that when the ball is cen-" ing the foreign matter and causing it to pass on through.

The tapered construction of the guides further assists in preventing wedging of particles between the ball and the guides.

The stop portion 34 is supported with respect to the .main body of the upper plate 24 by the narrow Web portions as which serve to subdivide the upper ends of each passageway 32 into quadrant-like areas or openings 37 in the top surface of the upper plate member. The thickness of the web portions 36 should be held to the minimum thickness possible, consistent with the strength of the material of which the plate member is constructed, .and t e same is true of the size of the stop portion 34, which is located at and formed by the juncture of the web portions. In other words, the area of stop portion 34 should be significantly less than the diametral cross-sectional area of the ball 27, so that the quadrant-like openings 37 permit gas moving back therethrough in paths parallel with the axis of passageway 32 toward the ball, to strike the ball.

From the description thus far, it will be seen that the guides 33 and passageway 32 serve in effect to form bypass paths which connect with the upper end of the surface 29 and will serve to permit gas to move past the ball toward the outlet openings defined by areas 37 when the ball is unseated from its seat 29. The total crosssectional area of openings 37 should be made slightly greater than the minimum cross-sectional area occurring between the surface of the ball and the wall of passageway 32 when the ball is in its upper or lifted position. The purpose in this is to provide that once the gas moves past the midpoint of ball 27 it will gradually be reduced in velocity and, accordingly, increase again in pressure. The tapered construction of the guides 33 assist in achieving a smooth transition from one flow cross section to the ot er.

It will be noted that the underside of the stop portion 34, that is, the surface thereof confronting the ball 27, is slightly dished with the center of the concavity in line with the axis of movement of the ball. This concavity, in cooperation with the curved transition 33b between the straight portions of the guides 33 and the stop portion, assists in centering the ball axially with respect to its seat 28 when the ball moves into the raised position. Upon reversal of flow, the ball then tends to quickly seat with a minimum of bouncing from one edge of the seat to the other.

To assist the ball in returning to its seat, it may be desired to include a return spring 40. I have found that in many high speed compressors, a spring is not absolutely necessary since the flow of the gas is controlled sufiiciently by the construction hereinbefore set forth, as to insure that the ball will quickly seat during suction stroke. The reasons for this will subsequently appear. However, under cer ain conditions of operation in high speed, high capacity compressors, springs may be needed and the present design provides therefor.

The springs it? differ from the usual simple compression spring in that they are formed into an essentially conical configuration, that is, the convolutions increase in diameter from one end toward the other. The increase in diameter from one turn to the next is such that when compressed, the convolutions are capable of nesting within one another, thus permitting compaction of all turns into essentially coplanar relationship where the thickness of the compacted spring is equal to the thickness of the wire from which it is composed. Preferably the diameters of the successive convolutions are such that there will be space between them when compacted.

As shown in FIGS. 5 and 6, the smaller end of each spring 49 engages the ball while the large end bears against the curved transition portions 33a of the guides 33, spaced around stop portion 35. The ball is free to move upwardly against the stop portion, thus collapsing the smaller convolutions within the larger ones. The diameter of the convolution which engages the ball, that is, the smallest end of the spring, is such that it will provide for seating of the ball against the stop without pinching the spring therebetween.

In order to aid in the flowing of the gases past the valve, the inlet passageways 26 are provided with an upwardly tapering bore, which has the effect of gradually increasing the flow velocity of the gas as it approaches the bail area. The increase in flow velocity is, of course, of aid in obtaining a smooth and relatively non-turbulent flow past the ball and consequently assists materially in loss of velocity head.

The operation of the discharge valve illustrated in FIGS. 1-6, inclusive, should be evident from the foregoing description. During the suction stroke of thepiston, the balls 27 remain seated on the seats 2%; since the back pressure from the discharge load exerts a downward force on the balls. Where springs 4d are employed, the springs assist in holding the balls seated, although the springs are not the principal seating force. The seated position of balls 27 is illustrated in solid lines in FIGS. 4 and 5. On the upstroke of the piston, the gases in the cylinder compress and, as a result, the balls are lifted from their seats to the positions illustrated in broken lines in FIGS. 4 and 5. The lifting of the ball elements opens the flow paths past the balls and seats, permitting the gas to move upwardly through the inlets past the balls and through the passageways 3t and 32 to. the outlets 37. The

balls remain in the upper or lifted position during the gases which are attempting to return toward the cylinder are guided by the curved surface or" ball 27 and the curved surface 29 adjacent the seat to provide a confined flow which is guided parallel with or follows the curvature of the surface of the ball. Since this flow exerts little pressure inhibiting return of the ball, the ball will immediately seat.

Turning now to FIGS. 7, 8 and 9, the embodiment of the invention therein shown is in the form of a suction valve. As will be understood by those versed in the compressor art, compressor pistons are conventionally provided in the working end thereof with threaded apertures in which suction valves of the general type here involved can be secured. The bottom or lower end of the valve is exposed beneath the working face of the piston and the top of the valve is usually flush with the working face and forms a part thereof.

As shown, the main body of the suction valve includes the threaded circular valve base Ilti]. which is adapted to be threaded in conventional fashion into the piston aperture previously described. Provided on the upper portion of the base 101 is circular flange 163112, the under surface of which seats on the margin of the piston aperture (not shown). The flange 101a is provided with a pattern of concentric striations which form ridges 101b, which, when screwed into contact with the margin of the piston aperture, serve to effectively seal against leakage. Extending upwardly from flange 191a and integral therewith, is the upstanding flange or annular rim portion 101s.

Fitted into the recess formed by the rim portion 101:: and contacting the smooth planar upper face 181d of the ase is circular topb plate 162 which cooperates with the base member to form the completed valve assembly. The top member 102 is rigidly secured to the base 191 through the medium of radial dowel pins 103, which extend through receiving apertures title in the rim portion 10112 and have their inner ends received in pin receiving apertures 192a, formed in the edge of the top plate 102. While only one such pin is shown in FIG. 8, it will be understood that preferably two or more are used. The pins serve both to hold the top plate against axial separation from the base and to prevent twisting of the top plate with respect to the base.

It will be understood that pin apertures 10142 in rim portion 101a and the aligned recesses 102a in the top plate can be formed by drilling once the top plate is assembled in proper relationship with the base. The pins are then inserted. To hold the pins in position, a circumscribing annular strap 104 is heat shrunk onto the outer surface of rim portion 101C. The strap is further secured to the rim portion liilc by circumferentially spaced depressed areas or dimples idea in the strap which match with and are engaged in corresponding depressions 101 formed in the outer wall of the rim portion 10112.

The base N1 is provided like the bottom plate 25 of the preceding embodiment with a plurality of inlet passageways 12-5, each of which is belied at its lower end and which taper toward a recessed ball seat 128 at the upper end. Each seat is covered bya ball 127. The seatiorms the lower end of an arcuate surface 129 which terminates at its upper end in an opening in the upper face or" the base of greater diameter than the ball.

The top plate 102, like the top plate 24 of the pre ceding embodiment, is provided with passageways 132 and guides 133, identical in construction with those of the preceding embodiment. The only difference is that, for purposes of illustration, there are only three guides 133 in each passageway and the outlets are therefore divided into tripartite arrangement as at 37 rather than quadrants. Otherwise, the construction or" the flow guiding and controlling surfaces and the flow of gases therethrough is the same as that earlier described and it is believed that further description of the details as to the guide stops 13 and the like would be unnecessary repetition.

It will benoted thahby virtue of pinning the top plate 1% at its edges to the'rim petition 102b, the entire area amass? of the top plate is left free for flow passageways and is not impeded by any upward projections therefrom. In other words, no central bolt is required to clamp the top plate to the base, which is the case in all other valves of which i am aware. Furtherfore, the rim portion ltilc can be provided with vertical recesses ltllg into which can be inserted the lugs of a suitable twisting tool (not shown) for screwing the valve into and out of the piston. By virtue of this arrangement, at no time is any twist applied to the top plate 192 and thus there is no tendency for the plate to be shifted out of proper alignment on the base.

In the operation of the suction valve, the balls 127 remain seated on seats 128 during the compression stroke of the piston, since the compressed gas communicated through openings 137 exerts a downward force on the balls and the inertia of the balls during the upstroke of the piston and valve tends to maintain them seated. The seated position of balls 127 is illustrated in solid lines in FIG. 9. At the top of the stroke the direction of movement of the valve body is reversed and, as a consequence, the balls 127 are lifted from the seat and rise when pressure reversal occurs until they are engaged by stops 134. The lifting of the ball elements opens the flow paths past the balls and seats, permitting gas to move upwardly through the inlets 12;? past the balls and through passageways 132 in the smooth, guided, carefully controlled flow described in connection with the preceding embodiment, with all of the advantages in kinetic energy conservation attendant thereupon. The halls remain in the upper or lifted position during the remaining downstroke of the piston thus permitting the space above the piston to be charged with gas from below the valve. At the bottom of the downward or suction stroke, the reversal of direction of movement of the valve body coupled with the compression of the gas above the valve causes the balls 127 to again seat. As in the previous embodiment, the carefully guided flow and the elimination of any surfaces which would cause the reverse flow to .tend to hold the ball off the seat permits rapid seating.

This is of extremely great importance in compressors operating at very lo suction pressures.

From the foregoing it will be evident that l have accomplished all of the ends and objectives hereinbefore set forth. The manner of construction of the gas outlets is such that inclusion of far more balls in the valves than in the case of known structures is accomplished and, as a consequence, small diameter balls can be employed to advantage. The volume of the top plate which must be cut away to provide passage for the gas is held to a minimum, thus preserving the strength of the top plate. The advantage of being able to use a large number of small balls will be more apparent when it is understood that in any ball-type valve the area of the flow path between the ball and seat is a linear function of the diameter of the ball. Assuming the same lift, two balls of one-half the diameter of a single ball will provide a flow path of equal size with that provided by a single ball. However,

, two balls of one-half the diameter of the single ball will weigh considerably less than the single ball (assuming that they are of the same density) and since reversing energy loss is a function of mass, decrease in this type of loss will be evident.

It will be understood that certain features and subcorn binations are of utility and may be employed withoutrefi erence to other features and subcombmations. This is contemplated by and is within the scope of the claims.

fining an upper face and a lower face, a plurality of spaced, parallel gas inlet passageways extending from said lower face into said base member with theiraxes normal to said faces, each inlet passageway terminating at its upper end in a seat which is spaced below said upper surface, a plurality of concave recesses in the upper face of said base member, one for each passageway, each said recess being coaxial with its associated inlet passageway and forming an upward continuation of said inlet passageway from said seat, a ball member in each recess of a diameter greater than the seat, the concavity of the recess being such that its surface forms with the surface of the ball an annular axially curved space proceeding upwardly from the seat toward said upper face and increasing in cross-sectional area as it approaches said upper face, a top plate member superimposed on said base member and having a plurality of parallel cylindrical passageways aligned with and forming upward continuations from the upper ends of said recesses, the diameter of each said passageway being substantially equal to the diameter of the upper end of its associated recess, ball guide fingers arranged around the wall of each cylindrical passageway and extending inwardly therefrom and longitudinally thereof, the combined cross-sectional area of said guide lingers in the direction of flow being appreciably less than the cross-sectional area open to flow therebetween, the inner surfaces of said fingers merging toward one another above the ball to form a stop portion centrally spaced above the ball when the latter is in its seat, the merging portions of said guide fingers defining therebetween with the upper end of said cylindrical passageways sector like openings through which gas can exit from the cylindrical passageways.

2. The combination as in claim 1 wherein the area of said openings is at least equal to the minimum area of the flow path between the surface of the ball and said cylindrical passageway.

3. The combination as in claim 1 including a conical compression spring interposed between said ball and the .ierging portions of said guide fingers, the convolutions of said spring being collapsible within one another.

4. In a unidirectional flow control valve for high speed gas compressors, the combination of a base member having a planar face of substantial area, a plurality of concave smoothly curved recesses in said face, each recess haviru a circular opening in the base defining a seat, a plurality of inlet passageways, one for each recess, cxtending through said base member and terminating at said seat, a ball in each recess of greater diameter than the seat, the configuration of each recess being such that the wall of each recess is increasingly spaced from the ball as it approaches the upper end of the recess, a top plate member superimposed on said face and covering said balls, that side of the top plate member confronting the balls having a ball cavity for each ball, each said cavity havinga central stop portion for the ball spaced above and permitting limited axial movement of the'ball away from the seat, each said cavity further having a major cylindrical inside wall coaxial with the seat and of greater diameter than the ball with a plurality of narrow guide fingers extending inwardly from said wall toward the ball, said fingers and stop portion being integral with one an other and defining outlet openings in the top plate member above the cavity which lies axially within the circumference of the inside wall of said cavity.

5. The combinationas in claim 4 including a conical fcompression spring disposed coaxially between the ball and stop portion in each cavity, the convolutions of the spring capable of nesting within one another during lifting of the ball from the seat,

6. In a unidirectional flow control valve for gas compressors, the combination of a base member having a threaded portion on one side and formed with an upstanding annular flange on the other side circumscribing a face,

' a top member having an edge portion adjacent and within said flange, cooperating gas flowpassageways extending through said base member and top member, valving elements within said passageways operable to permit gas flow in one direction only, and a plurality of pin elements extending through lateral openings in said flange into apertures in said edge of said topmember whereby to maintain said top member secured against separation from said base member and twisting with respect thereto.

7. The combination as in claim 6 including a retaining ring surrounding the outer wall of said flange and engaging the outer ends of said pins.

8. The combination as in claim 7 wherein said ring is provided with inwardly projecting portions received in corresponding recesses in said outer wall of the flange.

9. The combination as in claim 6 wherein the top of said flange is provided with a series of peripherally spaced recesses extending downwardly into the body of the flange and adapted for insertion therein of the lugs of a twisting tool.

10. In a undirectional flow control valve for high speed gas compressors, the combination of a base member having opposed, parallel surfaces of substantial area defining an upper face and a lower face, a plurality of spaced, parallel gas inlet passageways extending from said lower face ito said base member with their axes normal to said faces, each inlet passageway terminating at its upper end in a seat which'is spaced below said upper surface, a plurality of concave recesses in the upper face of said base member, one for each passageway, each said recess being coaxial with its associated inlet passageway and forming an upward continuation of said inlet passageway from said seat, a ball member in each recess of a diameter greater than the seat, the concavity of the recess being such that its surface forms with the surface of the ball an annular axially curved space proceeding upwardly from the seat toward said upper face and increasing in cross-sectional area as it approaches said upper face, a top plate member superimposed on said base member and having a plurality of parallel cylindrical passageways aligned with and forming upward continuations from the upper ends of said recesses, the diameter of each passageway being substantially equal to the diameter of the upper end of its associated recess, ball guide fingers arranged around the wall of each cylindrical passageway and extending inwardly therefrom and longitudinally thereof, said guide fingers increasing in transverse cross-sectional area upwardly from the said recess and the combined cross-sectional area of said guide fingers in the direction of fiow being appreciably less than the cross-sectional area open to flow therebetween, the inner surfaces of said fingers merging toward one another above the ball to form a stop portion centrally spaced above the ball when the latter is in its seat, the merging portions of said guide fingers defining therebetween with the upper end of said cylindrical passageways sector-like openings through which gas can exit from the cylindrical passageways.

11. In a unidirectional flow control valve for high speed gas compressors, the combination of a base member having opposed parallel surfaces of substantial area defining an upper face and a lower face, a plurality of spaced, parallel gas inlet passageways extending from said lower face into said base member with their axes normal to said faces, each inlet passageway terminating at itsupper end in a seat which is spaced below said upper surface, a plurality of concave recesses in the upper face, of said base member, one for each passageway, each said recess being coaxial with its associated inlet passageway and forming an upward continuation of said inlet passageway from said seat, a ball member in each recess of a diameter greater than the seat, the concavity of the recess being such that its surface forms with the surface of the ball an annular axially curved space proceeding upwardly from the seat toward said upper face and increasing in cross-sectional area as it approaches said upper face, a top plate member superimposed on said base member and having a plurality of parallel cylindrical passageways aligned with and forming upward continuations from the upper ends of said recesses, the diameter of each said passageway being substantially equal to the diameter of the upper end of its associated recess, ball guide fingers arranged around the wall of each cylindrical passageway and extending inwardly therefrom and longitudinally thereof, the combined cross-sectional area of said guide fingers in the direction of flow being appreciably less than the cross-sectional area open to flow therebetween, the innersurfaces of said fingers merging toward one another above the ball to form a stop portion centrally spaced above the ball when the latter is in its seat, the merging portions of said guide fingers defining therebetween with upper end of said cylindrical passageways sector-like openings through which gas can exit from the cylindrical passageways, said base member including an annular flange circumscribing the edge of said top plate member, assembly pins extending laterally through said flange edgewise into said plate member, and a ring member carried by the base member disposed around said flange to engage the outer ends of said pins.

References Cited in the file of this patent UNITED STATES PATENTS 1,213,652 Johnson Jan. 23, 1917 1,220,872 Meyer Mar. 27, 1917 1,228,336 McClelland May 29, 1917 1,483,153 Baker Feb. 12, 1924 1,958,219 Voss May 8, 1934 2,124,323 Voss July 19, 1938 2,803,424 McCabe Aug. 20, 1957 2,865,398 Popovich Dec. 23, 1958 FOREIGN PATENTS 107,694 Switzerland of 1924 

1. IN A UNDIRECTIONAL FLOW CONTROL VALVE FOR HIGH SPEED GAS COMPRESSORS, THE COMBINATION OF A BASE MEMBER HAVING OPPOSED PARALLEL SURFACES OF SUBSTANTIAL AREA DEFINING AN UPPER FACE AND A LOWER FACE, A PLURALITY OF SPACED, PARALLEL GAS INLET PASSAGEWAYS EXTENDING FROM SAID LOWER FACE INTO SAID BASE MEMBER WITH THEIR AXES NORMAL TO SAID FACES, EACH INLET PASSAGEWAY TERMINATING AT ITS UPPER END IN A SEAT WHICH IS SPACED BELOW SAID UPPER SURFACE, A PLURALITY OF CONCAVE RECESSES IN THE UPPER FACE OF SAID BASE MEMBER, ONE FOR EACH PASSAGEWAY, EACH SAID RECESS BEING COAXIAL WITH ITS ASSOCIATED INLET PASSAGEWAY AND FORMING AN UPWARD CONTINUATION OF SAID INLET PASSAGEWAY FROM SAID SEAT, A BALL MEMBER IN EACH RECESS OF A DIAMETER GREATER THAN THE SEAT, THE CONCAVITY OF THE RECESS BEING SUCH THAT ITS SURFACE FORMS WITH THE SURFACE OF THE BALL AN ANNULAR AXIALLY CURVED SPACE PROCEEDING UPWARDLY FROM THE SEAT TOWARD SAID UPPER FACE AND INCREASING IN CROSS-SECTIONAL AREA AS IT APPROACHES SAID UPPER FACE, A TOP PLATE MEMBER SUPERIMPOSED ON SAID BASE MEMBER AND HAVING A PLURALITY OF PARALLEL CYLINDRICAL PASSAGEWAYS ALIGNED WITH AND FORMING UPWARD CONTINUATIONS FROM THE UPPER ENDS OF SAID RECESSES, THE DIAMETER OF EACH SAID PASSAGEWAY BEING SUBSTANTIALLY EQUAL TO THE DIAMETER OF THE UPPER END OF ITS ASSOCIATED RECESS, BALL GUIDE FINGERS ARRANGED AROUND THE WALL OF EACH CYLINDRICAL PASSAGEWAY AND EXTENDING INWARDLY THEREFROM AND LONGITUDINALLY THEREOF, THE COMBINED CROSS-SECTIONAL AREA OF SAID GUIDE FINGERS IN THE DIRECTION OF FLOW BEING APPRECIABLY LESS THAN THE CROSS-SECTIONAL AREA OPEN TO FLOW THEREBETWEEN, THE INNER SURFACES OF SAID FINGERS MERGING TOWARD ONE ANOTHER ABOVE THE BALL TO FORM A STOP PORTION CENTRALLY SPACED ABOVE THE BALL WHEN THE LATTER IS IN ITS SEAT, THE MERGING PORTIONS OF SAID GUIDE FINGERS DEFINING THEREBETWEEN WITH THE UPPER END OF SAID CYLINDRICAL PASSAGEWAYS SECTOR LIKE OPENINGS THROUGH WHICH GAS CAN EXIT FROM THE CYLINDRICAL PASSAGEWAYS. 